US4431049A - Bayonet tube heat exchanger - Google Patents

Bayonet tube heat exchanger Download PDF

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Publication number
US4431049A
US4431049A US06/196,626 US19662680A US4431049A US 4431049 A US4431049 A US 4431049A US 19662680 A US19662680 A US 19662680A US 4431049 A US4431049 A US 4431049A
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US
United States
Prior art keywords
fluid
hot gas
ducts
tube
shell
Prior art date
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Expired - Lifetime
Application number
US06/196,626
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English (en)
Inventor
Jun Zamma
Yoshinori Nishimura
Youichi Nakajima
Tadaaki Sakai
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Toyo Engineering Corp
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Toyo Engineering Corp
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Publication date
Application filed by Toyo Engineering Corp filed Critical Toyo Engineering Corp
Assigned to TOYO ENGINEERING CORPORATION reassignment TOYO ENGINEERING CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: NAKAJIMA YOUICHI, NISHIMURA YOSHINORI, SAKAI TADAAKI, ZAMMA JUN
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/021—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers with heating tubes in which flows a non-specified heating fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/12—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements

Definitions

  • the present invention relates to an improved heat exchanger using bayonet tubes and more particularly an improved heat exchanger free of thermal stress, comprising bayonet tube outer ducts which are open at and secured to a tube sheet of the heat exchanger and bayonet tube inner ducts which are open to and secured to a high temperature fluid separation chamber of the heat exchanger.
  • heat exchangers are used for the recovery of heat from high temperature gas generated as a result of burning, a reaction or the like.
  • Normal heat exchangers conventionally used are such as those shown in FIG. 1, and comprise a shell 1 containing a plurality of tubes 2 therein, the ends of the shell 1 being enclosed by tube sheets 3, 3 with the tubes 2 passing through the tube sheets and opened to chambers which are enclosed by the stationary heads 4,4 and the tube sheets 3,3.
  • the shell 1 is provided with an inlet nozzle 5 and an outlet nozzle 6 for the first fluid.
  • the stationary head 4 on one side of the shell is provided with an inlet nozzle 7 for the second fluid, and the stationary head 4 on the other side is provided with an outlet nozzle 8 for the second fluid.
  • the shell 1 is in contact with the first fluid, while the tubes 2 are in contact with the second fluid.
  • the temperature difference therebetween causes a change in relative thermal expansion between the shell 1 and the tubes 2.
  • Thermal stress is thereby induced at the connection between the tubes 2 and the tube sheets 3 and at the connection between the shell 1 and the tube sheets 3.
  • the temperature difference also exists between the inner and outer surfaces of the tube sheets 3.
  • the thermal stress caused by those temperature conditions often makes the design of heat exchangers of this type difficult. Further, the places where thermal stress arises as mentioned above are located where inspection as well as repair is difficult to perform.
  • the middle portion of the shell In order to absorb the thermal expansion it is possible to provide the middle portion of the shell with an expansion joint 9.
  • the first fluid is a hot gas
  • insulation materials which are lined on the shell wall would separate therefrom due to the expansion and contraction of the shell 1.
  • the aforementioned first fluid is water, high pressure steam exceeding 100 atoms is normally generated, thereby rendering the mechanical design of expansion joints very difficult.
  • FIG. 2 Another type of conventionally used heat exchangers is shown in FIG. 2. It comprises a shell 1 having an inlet nozzle 5 and an outlet nozzle 6 for the first fluid wherein U tubes 2a are contained, the ends of the U tubes 2a passing through a tube sheet 3 and being open to a chamber defined by a tube sheet 3, a stationary head 4a and a chamber cover 4b.
  • the chamber is separated into two volumes by a pass partition 10, one volume being provided with an inlet nozzle 7 for the second fluid and an open port of one end of each of the U tubes 2a, the other volume being provided with an outlet nozzle 8 for the second fluid and an open port of the other end of each of the U tubes 2a.
  • the object of the present invention is to solve the aforementioned problem and provide a safe and economic heat exchanger of novel design, which uses bayonet tubes and a chamber for fluid before heat exchanging, a chamber for fluid after heat exchanging.
  • Another object of the present invention is to eliminate the thermal stress caused by the difference of thermal expansion between tubes and a shell, permitting a design using tube sheet and a shell and using low cost materials other than high grade steel.
  • Still another object of the present invention is to provide a light weight and low cost heat exchanger, which can be designed with the rational use of thermal insulation material to operate in the temperature range where the material strength is not lowered.
  • FIG. 1 shows a schematic section of an example of conventional heat exchangers
  • FIG. 2 is a schematic section of another example of conventional heat exchangers
  • FIG. 3 is a schematic section of an embodiment of heat exchangers according to the present invention.
  • FIG. 4 is a schematic section of another embodiment of heat exchangers according to the present invention.
  • FIG. 3 a schematic section of an embodiment of heat exchangers according to the present invention.
  • This is an embodiment of heat exchanger which uses hot gas for the first fluid and high pressure cold gas for the second fluid.
  • the device generally comprises a cylindrical shell 11 which is provided with an inlet nozzle 12 and outlet nozzle 12a for the first fluid and is enclosed except the outlet nozzle 12a at one end and connected to a tube sheet 13 at the other end.
  • Normally Cr-Mo steel, heat resisting steel or the like is used for the shell 11, the inside of which is lined normally with heat insulation material 14 if the operating temperature exceeds the upper limit for the material used.
  • the shell 11 contains a plurality of bayonet tube outer ducts 15, one end of each of which passes through the tube sheet 13 and is secured to the tube sheet 13, opened to the outside of the shell 11, while the other end thereof is closed.
  • a plurality of baffle plates 16 for controlling the flow of the first fluid, and a shroud 17 adjacent to the tube sheet 13.
  • the side of the tube sheet 13 opposite to the shell 11 is connected to a stationary head 18, the end of which is enclosed by a chamber cover 19, with the tube sheet 13, the stationary head 18 and the chamber cover 19 altogether forming a tube side pressure chamber 28.
  • the stationary head 18 is provided with an exit nozzle 20 for the second fluid
  • the chamber cover 19 is provided with an inlet nozzle 21 for the second fluid.
  • a hot gas separation chamber 27 which is separated therefrom by the tube sheet 22 and head cover 23.
  • Bayonet tube inner ducts 24 connected to the hot gas separation chamber 27 are inserted through the tube sheet 22 into the bayonet tube outer ducts 15, with an annular space being provided between the inner ducts 24, and outer ducts 15.
  • the open end of each of the inner ducts 24 inside the outer ducts 15 is provided with a clearance from the end of each of the outer ducts 15 permitting fluid to flow, while the other end of inner duct 24 at the side of tube sheet 22 is opened to the hot gas separation chamber 27.
  • the hot gas separation chamber 27 is connected to the inlet nozzle 21 for the second fluid through a gas inlet duct 25, which is provided with an expansion joint 26 if necessary.
  • hot gas as the first fluid is introduced through the inlet nozzle 12 into the shell 11, flows through the inter-duct spaces defined by the outer ducts 15, and while changing its direction of flow by the baffle plates and being cooled through heat exchanging, leaves the device through the outlet nozzle 12a for the first fluid.
  • high pressure cold gas enters into the hot gas separation chamber 27 through the inlet nozzle 21 for the second fluid, flows into the bayonet tube inner ducts 24 opening at the tube sheet 22 and out through the other ends of the ducts 24 into the outer ducts 15, proceeds through the annular spaces between the innerducts 24 and the outer ducts 15 while exchanging heat with the first fluid through the wall of the outer ducts 15 and being heated up, flows further into the tube side pressure chamber 28 through the openings at the tube sheet 13, and leaves the device from the outlet nozzle 20 for the second fluid.
  • the hot gas separation chamber 27 which is contained inside the tube side pressure chamber 28, is exposed to the high pressure second fluid on its inner wall surface as well as its outer wall surface, the pressure difference between the inside and outside of the chamber 27 being equal to the pressure drop of the second fluid flowing through the inner ducts 24 and outer ducts 15.
  • the hot gas separation chamber 27 therefore can be constructed with thin plates, being made extremely light weight, since the strength of the gas separation chamber 27 needs only to withstand the pressure equivalent to the aforementioned pressure drop.
  • the fluid inlet duct 25 and the expansion joint 26 can also be made of thin materials as well. The arrangement of flowing the same fluid in the inner duct and reversely in the space between the inner and outer duct sometimes is not preferred from the point of performance design of heat exchangers.
  • thermal loss can be prevented by using thermally insulated tubes for the inner ducts 24 such as a ceramic or composite tube which consists of two coaxial tubes filled with insulated material therebetween.
  • Single or multiple shrouds 17 installed inside the shell 11 can restrict convective heat transfer of hot gas as the first fluid to the wall of tube sheet, preventing excessive temperature rise on the wall of the shell side of the tube shell 13.
  • the temperature of high pressure gas as the second fluid at the location where it passes through the tube sheet 13 after being heated is generally lower than the temperature of hot gas as the first fluid at the outlet nozzle 12a of the shell 11, and such irregular temperature gradient does not occur in the tube sheet 13 as in the device in FIG. 2 using U tubes 2a, and therefore excessive thermal stress is not induced in the tube sheet designed for high pressure.
  • the shell 11 and the group of ducts 24 are thermally insulated by the bayonet tubes, so the thermal stress due to the difference in thermal expansion does not occur.
  • Hot gas is let in through the outlet nozzle 12a, exchanges heat through the bayonet tube outer ducts 15 and, after changing its direction by the baffle plates 16 and being cooled, flows out of the device through the inlet nozzle 12.
  • high pressure cold gas is introduced into the device through the outlet nozzle 20, flows through the annular openings provided at the tube sheet 13 between the outer ducts 15 and inner ducts 24 of the bayonet tubes into the annular spaces between the above two ducts and, after exchanging heat with the hot gas, enters into the hot gas separation chamber 27 through the inner ducts 24, leaving the device through the inlet nozzle 21.
  • this method is used, the tube sheet 13 is exposed to the hot gas after cooling and to the high pressure cold gas before exchanging heat, thus preventing excessive temperature rise on the tube sheet 13.
  • the use of the aforementioned shroud 17 can further suppress the temperature rise, thereby preventing problems of design and materials from arising.
  • This embodiment is a vertical waste heat boiler of the integral steam drum type.
  • the boiler generally comprises a cylindrical pressure proof shell 31 which is provided with a steam outlet nozzle 32 and a water feed nozzle 33. Inside the shell 31 are provided an impact plate 34 and demister 35 near the lower end of the steam outlet nozzle 32. The lower end of the shell 31 is connected to a tube sheet 36, through which a plurality of bayonet tube outer ducts 37 pass, with the ducts 37 being secured to the tube sheet 36.
  • the bayonet tube outer ducts 37 extend into the inside of the shell 31, the ends of the outer ducts 37 being closed and the other ends thereof being open at the lower surface of the tube sheet 36.
  • Inside the shell 31 is provided an inner shell 38 encircling the group of bayonet tubes with a clearance about them.
  • a tube side pressure chamber 41 is formed by a stationary head 39 and a chamber cover 40.
  • the stationary head 39 is provided with a hot gas outlet nozzle 42 and the chamber cover 40 is provided with a hot gas inlet nozzle 43.
  • the inner wall surface of the tube side pressure chamber 41 is usually lined with insulation materials 44.
  • the tube side pressure chamber 41 contains inside thereof a hot gas separation chamber 47 which is enclosed by a thin tube sheet 45 and a head cover 46, the bottom of the head cover 46 being connected to the hot gas inlet nozzle 43 through the gas inlet pipe 48.
  • a plurality of bayonet tube inner ducts 49 are secured to the thin tube sheet 45 and opened to the hot gas separation chamber 47, the inner ducts 49 extending to the upper side of the tube sheet 36 and being inserted inside the outer ducts 37 with an annular space provided therebetween, with the top end of the inner ducts 49 leaving a clearance from the closed top end of the outer ducts 37 to admit gas flow.
  • the hot gas separation chamber 47 and the hot gas inlet pipe 48 are usually covered with insulation materials.
  • the tubes are made free to expand and contract through the use of bayonet tubes and hot gas separation chamber and so no thermal stress is induced, which are conventionally caused by the difference of thermal expansion between the tubes and the shell.
  • the hot gas separation chamber 47 is contained in the interior of the tube side pressure chamber 41, permitting the provision of a mechanical design based on the pressure drop, thereby leading to the construction of an extremely light weight device.
  • the hot gas separation chamber 47 also is independent from the tube side pressure chamber 41, giving no thermal effect on the tube side pressure chamber 41 if provided with some amount of insulation work.
  • the tube side pressure chamber 41 and the tube sheet 36 can be designed on the basis of an exit gas temperature of about 500° C. Further, if thermal insulation is provided on the inner wall of stationary head 39, it can be constructed with Cr-Mo steel or C1/2 Mo steel even though the involvement of hydrogen fume is taken into consideration, rendering the use of expensive heat resistant steel unnecessary.
  • the present invention can be applied to a horizontal waste heat boiler, in which a steam drum is separated, it being possible to take this configuration if required from the layout of equipment and ease of maintenance.
  • a heat exchanger As mentioned above, in a heat exchanger according to the present invention, such construction is used to permit free thermal expansion of a duct group of bayonet tubes relative to its drum so that the thermal stress caused by the difference in thermal expansion between the tubes and shell is prevented and a thick tube sheet in contact with a shell is not exposed to high temperature and has uniform temperature distribution, making the design and selection of material very advantageous.
  • the tube side pressure chamber is thermally separated from the second fluid by the provision of a hot gas separation chamber, and therefore structural design and prevention of corrosion are made much easier.
  • the hot gas separation chamber also can be structurally designed on the basis of differential pressure of the second fluid across a heat exchanger and additionally, the use of thermal insulation permits the design for temperature range where material strength is not lowered.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US06/196,626 1979-11-27 1980-10-14 Bayonet tube heat exchanger Expired - Lifetime US4431049A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP54-152432 1979-11-27
JP15243279A JPS5677692A (en) 1979-11-27 1979-11-27 Heat exchanger

Publications (1)

Publication Number Publication Date
US4431049A true US4431049A (en) 1984-02-14

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US (1) US4431049A (enrdf_load_stackoverflow)
JP (1) JPS5677692A (enrdf_load_stackoverflow)
DE (1) DE3039787A1 (enrdf_load_stackoverflow)
GB (1) GB2064091A (enrdf_load_stackoverflow)
IN (1) IN153892B (enrdf_load_stackoverflow)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4547341A (en) * 1983-12-08 1985-10-15 Exxon Research And Engineering Co. Cyclone support system
US4585053A (en) * 1982-09-02 1986-04-29 The United States Of America As Represented By The United States Department Of Energy Heat exchanger for reactor core and the like
US4656001A (en) * 1981-02-24 1987-04-07 Stein Industrie Societe Anonyme Device for the homogeneous mixing of liquids flowing at different temperatures
US4700773A (en) * 1985-09-18 1987-10-20 Borsig Gmbh Nested-tube heat exchanger
US4889182A (en) * 1981-09-08 1989-12-26 The Dow Chemical Company Heat exchanger
US5035283A (en) * 1989-09-09 1991-07-30 Borsig Gmbh Nested-tube heat exchanger
WO1996010158A1 (en) * 1994-09-26 1996-04-04 Stellan Grunditz Heat exchanger
EP0860673A3 (en) * 1997-02-21 1999-03-24 Haldor Topsoe A/S Synthesis gas waste heat boiler
US5940987A (en) * 1996-04-17 1999-08-24 Andritz-Patentverwaltungs-Gesellschaft M.B.H. Heat exchanger with concentric tubes
US5954128A (en) * 1996-03-06 1999-09-21 Solar Turbines High pressure ceramic heat exchanger
US6431261B2 (en) * 1999-12-28 2002-08-13 Nippon Shokubai Co., Ltd. Shell and tube type heat exchanger
US20060065014A1 (en) * 2004-09-29 2006-03-30 Chevron U.S.A. Inc. Method for recovering LPG boil off gas using LNG as a heat transfer medium
WO2011107841A1 (en) * 2010-03-03 2011-09-09 Alstom Technology Ltd Heat exchanging and liquid separation apparatus
US20120193082A1 (en) * 2011-01-31 2012-08-02 Hoest-Madsen Svend Heat exchanger
WO2013026258A1 (zh) * 2011-08-19 2013-02-28 汇堡国际有限公司 热交换器、包括该热交换器的能源回收装置及能源回收系统
US20130153171A1 (en) * 2011-12-14 2013-06-20 Lockheed Martin Corporation Composite heat exchanger shell and buoyancy system and method
NL2012221C2 (en) * 2014-02-06 2015-08-10 Solutherm B V Apparatus for desubliming or condensing a condensable fluid in a closed space.
CN106288923A (zh) * 2016-08-31 2017-01-04 上海电气电站设备有限公司 一种双通型换热器水室
US9823021B2 (en) 2012-05-24 2017-11-21 Kellogg Brown + Root LLC Methods and systems for cooling hot particulates
CN108758587A (zh) * 2018-05-03 2018-11-06 中广核研究院有限公司 一种用于金属快堆的蒸汽发生器
US20190293320A1 (en) * 2018-03-23 2019-09-26 Dongho Kim Extreme condensing boiler
CN113048816A (zh) * 2021-04-28 2021-06-29 北京广厦环能科技股份有限公司 一种立式蒸发器
US11054196B2 (en) 2017-05-26 2021-07-06 Alfa Laval Olmi S.P.A. Shell-and-tube heat exchanger
CN113446873A (zh) * 2020-03-24 2021-09-28 中国石化工程建设有限公司 U形管换热器
CN117419586A (zh) * 2023-12-19 2024-01-19 中国核动力研究设计院 一种单向微通道换热管组件及换热器

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LU84557A1 (fr) * 1982-12-24 1984-10-22 Echangeurs De Chaleur Sag S A Echangeur de chaleur en matieres thermoplastiques fluorees
GB8308343D0 (en) * 1983-03-25 1983-05-05 Ici Plc Steam reforming
JPS59191081U (ja) * 1983-06-06 1984-12-18 宇部興産株式会社 高温ガス受入部の冷却構造
GB2161596A (en) * 1983-06-13 1986-01-15 Humphreys & Glasgow Ltd Reactor for exothermic gas reactions
JPS60111869U (ja) * 1983-12-28 1985-07-29 日本鋼管株式会社 二重管式熱交換器の下部構造
JPH06103628B2 (ja) * 1986-02-14 1994-12-14 松下電器産業株式会社 鉛蓄電池
JPH0443734Y2 (enrdf_load_stackoverflow) * 1986-03-05 1992-10-15
DE3729757C2 (de) * 1987-09-02 2000-05-25 Atp Arbeit Tech Photosynthese Verfahren zur gravitationsbedingten Trennung der flüssigen von der gasförmigen Phase einer krustenbildenden Flüssigkeit
JP2630427B2 (ja) * 1988-05-20 1997-07-16 株式会社荏原製作所 セラミックス製バイヨネット式熱交換器
JP4051939B2 (ja) * 2002-01-28 2008-02-27 松下電工株式会社 脱臭装置
DE10223788C1 (de) 2002-05-29 2003-06-18 Lurgi Ag Wärmetauscher
JP4311023B2 (ja) * 2003-01-20 2009-08-12 パナソニック電工株式会社 脱臭装置
CN104697361B (zh) * 2015-03-18 2016-08-17 安徽工业大学 一种抗粘结自流焦炉荒煤气余热回收换热单元的施工方法
WO2019074084A1 (ja) * 2017-10-13 2019-04-18 株式会社奈良機械製作所 粉粒体の熱交換装置

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Publication number Priority date Publication date Assignee Title
US1014140A (en) * 1911-03-15 1912-01-09 Zenas U Dodge Ice-making apparatus.
GB122563A (en) * 1918-04-22 1919-01-30 Arthur Whitten Brown Improvements in Condensers and Coolers for Steam and other Fluids.
US2357156A (en) * 1942-03-02 1944-08-29 Mcquay Inc Radiator
US2423697A (en) * 1943-12-24 1947-07-08 Ice Air Conditioning Co Inc Method of assembling headers and tubes
US2499608A (en) * 1944-07-31 1950-03-07 Charles N Rink Heat exchange device
DE1000840B (de) * 1951-01-17 1957-01-17 Willi Posselt Waermeaustauschelement
US3201938A (en) * 1963-06-27 1965-08-24 Gen Electric Recuperative arrangement for gas turbine engines
US3850231A (en) * 1973-05-24 1974-11-26 Combustion Eng Lmfbr intermediate heat exchanger
US4078899A (en) * 1975-09-26 1978-03-14 Friedrich Uhde Gmbh Reaction vessel heated by helium
US4220200A (en) * 1976-11-12 1980-09-02 Sulzer Brothers Limited Heat exchanger system
US4142580A (en) * 1976-11-19 1979-03-06 Phillips Petroleum Company Bayonet heat exchanger having means for positioning bayonet tube in sheath tube
US4193447A (en) * 1976-12-21 1980-03-18 Sulzer Brothers Limited Heat exchanger for a high temperature reactor
GB1532757A (en) * 1977-09-23 1978-11-22 Sulzer Ag Heat exchanger system

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4656001A (en) * 1981-02-24 1987-04-07 Stein Industrie Societe Anonyme Device for the homogeneous mixing of liquids flowing at different temperatures
US4889182A (en) * 1981-09-08 1989-12-26 The Dow Chemical Company Heat exchanger
US4585053A (en) * 1982-09-02 1986-04-29 The United States Of America As Represented By The United States Department Of Energy Heat exchanger for reactor core and the like
US4547341A (en) * 1983-12-08 1985-10-15 Exxon Research And Engineering Co. Cyclone support system
US4700773A (en) * 1985-09-18 1987-10-20 Borsig Gmbh Nested-tube heat exchanger
US5035283A (en) * 1989-09-09 1991-07-30 Borsig Gmbh Nested-tube heat exchanger
WO1996010158A1 (en) * 1994-09-26 1996-04-04 Stellan Grunditz Heat exchanger
US5954128A (en) * 1996-03-06 1999-09-21 Solar Turbines High pressure ceramic heat exchanger
US5940987A (en) * 1996-04-17 1999-08-24 Andritz-Patentverwaltungs-Gesellschaft M.B.H. Heat exchanger with concentric tubes
EP0860673A3 (en) * 1997-02-21 1999-03-24 Haldor Topsoe A/S Synthesis gas waste heat boiler
US6431261B2 (en) * 1999-12-28 2002-08-13 Nippon Shokubai Co., Ltd. Shell and tube type heat exchanger
US20060065014A1 (en) * 2004-09-29 2006-03-30 Chevron U.S.A. Inc. Method for recovering LPG boil off gas using LNG as a heat transfer medium
WO2006039172A3 (en) * 2004-09-29 2007-03-01 Chevron Usa Inc Method for recovering lpg boil off gas using lng as a heat transfer medium
GB2434434A (en) * 2004-09-29 2007-07-25 Chevron Usa Inc Method for recovering LPG boil offgas using LNG as a heat transfer medium
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JPS5677692A (en) 1981-06-26
DE3039787A1 (de) 1981-06-04
IN153892B (enrdf_load_stackoverflow) 1984-08-25

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